Refrigeration



1941- H. M. ULLSTRAND. 2,252,791

REFRIGERATION Filed March 26, 1938 IN/ATTORNEY.

Patented Aug. 19, 1941 I UNITED STATES PATENT OFFICE REFRIGERATION Hugo M. Ullstrand, Evansville, Ind., aasignor to Serve], Inc., New You. Y., a corporation of Delaware Application March 2t, 1938, Serial No. 198,161

(01. era-119,5)

12 Claims.

gas fdrmed in evaporator l2 flows from the up- D r part thereof through a conduit 25. the inproved circulation of fluid in refrigeration"sys-- terns of this type to obtain better use of refrig crating or cooling effect. l

The above and other objects and advantages of the invention will be more fully understood upon reference tothe following description and the accompanying drawing forming a part of this.

trates more or less diagrammatically a refrigeration system embodying the invention.

In thedrawing I have shown my improvement embodied in a refrigeration system of a uniform pressure absorption type. Such a system includes a generator In, condenser ll, evaporator I 2, and an absorber l3 which are interconnected in a manner well-known in the art and which will briefly be described hereinafter. The system contains a solution of refrigerant in absorption liquid, such as ammonia in water for example, and also an inert gas or auxiliary agent, such as hydrogen.

The generator I0 is heated in any suitable manner, as by a gas burner, for example, to which a suitable combustible gas is delivered through a conduit l5. Due to heating by burner ll, refrigerant vapor is expelled from solution in generator Ill. The refrigerant vapor flows upwardly through standpipe l6 and conduit l1 into the aircooled condenser I l where the vapor is condensed into liquid.

The condenser ll includes an upper condenser section Ila and a lower condenser section Ilb. Refrigerant liquefied in upper condenser section Ila flows into a gas separating chamber It and thence through conduit l9 into evaporator 12. Refrigerant not liquefied in upper condenser section Ha flows from gas separating chamber l8 into the lower condenser section llb in which it is liquefied. Liquid refrigerant flows from lower condenser section 17 into gas separating chamber 20 and thence through conduit 21 into evaporator l2.

The evaporator 12 is arranged in a space or compartment 22-formed by thermally insulated walls 23. Refrigerant fluid in evaporator l2 evaporates and diffuses into inert gas which enters through a conduit 2|, thereby producing a refrigerating or cooling effect with consequent absorption of heat from the surroundings. The rich gas mixture of refrigerant vapor and inert specification, and in which the single figure illuser conduit 26 of a gas heat exchanger 21, and

conduit 28 into the lower part of absorber ii.

In" absorber IS the rich gasmixture flows counter-current to downwardly flowing weak absorptlon liquid which enters through a conduit 22. The absorption liquid absorbs refrigerant vapor from the inert gas, and inert gas weak in refrigerant vapor flows from absorber I! through a conduit 30, outer conduit ll of gas heat exchanger 21, and conduit 24 into the lower part of evaporator l2.

The circulation of gas in the gas circuit Just described is due to the difference in specific weight of the columns of rich and weak gas in the inner and outer conduits 26 and 31, respectively, of gas heat exchanger 21. Since the rich gas is heavier than the weak gas, force is produced for causing flow of rich gas toward absorber l3 and flow of weak gas toward evaporator 12.

Absorption liquid enriched in refrigerant flows from the lower part of absorber l2 through a conduit 32, outer passage of a liquid heat exchanger 23, and conduit 34 into generator in. Liquid is raised in the generator by a thermosiphon tube 35 to a higher level than the upper end of conduit 29 and flows back to the generator through stand-pipe l6. Refrigerant vapor expelled out of solution in generator Ill, together with refrigerant vapor entering through thermosiphontube 35, flows upwardly through standpipe l6 and conduit l1 to condenser II, as explained above.

The absorption liquid from which refrigerant has been expelled 'flows from generator I! through conduit 36, inner passage of liquid heat exchanger 33, and conduit 29 to the upper part of absorber l3. This circulation of absorption liquid is effected by raising liquid by means of thermosiphon tube 35. Heat liberated with absorption of refrigerant vapor in absorber I2 is transferred to a cooling medium which flows into a coil 31 arranged in thermal exchange relation with the absorber.

The lower end of condenser II is connected by a conduit 38, vessel 39, and conduit 40 to the gas circuit, as at the upper end of gas heat exchanger 21, for example, sot-hat any inert gas which may pass through the condenser can flowing upwardly therethrough in the presence 7 of and in counter-flow to liquid refrigerant which enters through conduits l9 and 2|. Since gas weak in refrigerant enters lower evaporator section l2b through conduit 24 and rich gas leaves upper evaporator section IZa through conduit 25, the gas in upper section [2a contains a greater amount of refrigerant vapor than the gas in lower section I217. The partial vapor pressure of refrigerant in the gas mixture formed in evaporator I2 is a gradient, so that the evaporating temperature of liquid refrigerant is also a gradient, the evaporating temperature of liquid being lower in lower evaporator section I221.

The upper evaporator section l2a is primarily employed for cooling space 22 and is provided with fins 4|, whereby a relatively extensive surface is provided for cooling air flowing over the surfaces thereof.

The lower evaporator section I2!) is provided with a limited heat transfer surface and employed as a freezing section for freezing ice cubes and the like. The lower evaporator section I2!) is diagrammatically shown in the form of a coil which may be embedded in or otherwise suitably arranged in thermal exchange relation with a shell 42 indicated in dotted lines. Such a shell usually is provided with a plurality of freezing compartments to receive trays for freezing water and other matter to be frozen.

The refrigeration system just described may be controlled by a thermal bulb 43 which is affected by a temperature condition of evaporator l2. As shown, the thermal bulb 43 is arranged in thermal exchange relation with the bottom part of lower evaporator section I21) and connected by a conduit 44 to a control device 45 which is connected in fuel supply conduit I5. The thermal bulb 43 and conduit 44 may form part of an expansible fluid thermostat which is charged with a suitable volatile fluid for operating control device 45 with changes in temperature of lower evaporator section l2b, in a manner well-known in the art.

When the temperature of lower evaporator section l2b increases due to an increase in load on the evaporator, the thermal bulb 43 becomes effective tooperate control device 45 to increase the supply of fuel to burner I4 and hence the heat input to generator Ill. Under these conditions refrigerant vapor is expelled from solution in generator l at an increased rate, thereby increasing the amount of refrigerant vapor which condenses in condenser I I and flows into evaporator l2. Conversely. when the temperature of lower evaporator section |2b decreases, the thermal bulb 43 becomes effective to operate control device 45 to decrease the supply of fuel to burner I 4 and hence reduce the heat input to generator I. Under these conditions, the rate at which refrigerant. vapor is expelled out of solution in generator J!) is reduced, thereby decreasing the amount of refrigerant vapor which condenses in condenser ll andflows into evaporator l2.

When trays containing water to be frozen are inserted in shell 42 of lower evaporator section 12b, liquid refrigerant may not be reaching the lower part of evaporator section i222. This may be reaching the lower part of evaporator section 12b because liquid is not flowing through conduit 2| and liquid flowing to evaporator I2 is first intfioduced into upper section [2a. If liquid refrigerant should not be reaching the lower part of lower evaporator section [2b, the thermal bulb 43 would normally become effective to increase the, heat input to generator [0, as explained above.

When the heat input to generator I0 is increased with the conditions assumed, the uniform temperature at which it is desired ot keep space 22 is disturbed. Thus, when the room temperature is low and the heat input to generator I!) is reduced, the refrigerating effect produced by evaporator I2 for space cooling may be adequate to keep space 22 at a desired low temperature at the time the freezing load is increased. When the heat input to generator I0 is increased in response to thermal bulb 43, due to lack of liquid in lower evaporator section I2b, more liquid will flow into the evaporator. In addition to supplying liquid to take care of the increased freezing load, additional space cooling will be effected to lower the temperature of space 22 below the desired value.

In accordance with this invention, I propose to better this situation by reducing the flow of liquid refrigerant to upper evaporator section lZa and flowing liquid directly to lower evaporator section |2b when the amount of liquid in the latter is not suflicient to take care of a freezing load. In the drawing I have diagrammatically shown one way of carrying out the invention.

At the lower end of lower evaporator section I21) I provide a vessel 46 into which liquid refrigerant can flow. The vessel 46 may be considered a part of lower evaporator section l2b and may also be embedded in or otherwise suitably arranged in thermal exchange relation with shell 42. To vessel 46 is connected one end of a drain conduit 41 which is bent to provide a liquid trap 48. The other end of conduit 41 is connected to the inner conduit 26 of gas heat exchanger 21, whereby excess liquid may be drained from lower evaporator section l2b. Instead of draining excess liquid directly from the bottom of lower evaporator section [2b in the usual manner, therefore, I provide the vessel 46 in which liquid accumulates to a predetermined level before draining into the gas heat exchanger 21.

To the bottom of vessel 46 is connected one end of a conduit 49 which is connected at itsother end to the bottom of a vessel50. The portion of conduit 49 adjacent vessel 50 is looped at 5| and provided with cooling fins to form an auxiliary condenser. A lower part of vessel 50 is connected by conduit 52 to conduit l1, and an upper part of the'vessel is connected by a conduit 53 to the upper part of chamber l8.

The conduit 52, vessel 50, and conduit 53 form a by-pass around upper condenser section Ha whereby refrigerant vapor flowing upwardly from generator Hi can pass directly to lower condenser section I lb. The vessels 46 and ill and connecting conduit 49 form a liquid trap.

When the amount of liquid accumulated in vessel 46 is such that the level of liquid in vessel 50 is above-the connection of conduit 52, the liquid in vessel 50 is effective to seal the by-pass for refrigerant vapor. With these conditions refrigerant vapor flows upwardly through conduit I1 and passes in series through condenser sections Ho and llb. All of the liquid entering evaporator 12 through conduit l9 flows first into upper evaporator section i241 and then into lower section I212, while any liquid entering through conduit 2| flows directly into lower section lib.

' When liquid in vessel 46 evaporates and diffuses I into inert gas at a'faster rate than the rate at which liquid flows into the vessel, the liquid level in vessel 46 will be lowered. This lowering of liquid level may occur when the freezing load is .the liquid level in vessel 46 is lowered so that the liquid levelin vessel 50 falls'sufiiciently to open the liquid seal, refrigerant vaporflowing from generator II) can flow through conduit 52, vessel 50, conduit 53, and chamber l8 directly into lower condenser section lib.

With refrigerant vapor flowing in parallel paths of flow through condenser sections I la and lib, less refrigerant condenses in upper section I la and more refrigerant condenses in lower section lib. The liquid formed in lower condenser section III; can flow directly into lower evaporator section l2b to take care of the freezing load. Since less refrigerant condenses in upper condenser section Ila under these conditions, less liquid flows to upper evaporator section l2a. With this arrangement, the refrigerating effect produced by lower evaporator section no can be increased and that produced by upper evaporater section IZa. can be decreased, so that an increase 'in freezing load can be taken care of without unnecessarily increasing the amount of space cooling effected by evaporator l2.

By providing auxiliary condenser 5i, refrigerant vapor is condensed in the liquid trap when operation of the refrigeration system is started, thereby preventing flow of refrigerant vapor from conduit l-I into the lower part of lower evaporator section lZb. During operation of the refrigeration system condenser 5| functions to insure liquid'remaining in the liquid trap. While a single embodiment of the invention has been shown and described, such variations and modifications are contemplated as fall within the true spirit and scope of the invention, as pointed cut in the following claims.

What is claimed is: 1. In .arefrigeration system, an evaporator,

. means to flow liquid to said evaporator at different elevations for downward flow through the latter, connections for circulating an auxiliary flowing refrigerant fluid selectively in series or in parallel through said places of condensation.

3. In a refrigeration system, an evaporator in- ,cluding upper and lower sections connected inorator section, and means for controlling said bypass connection.

4. In a. refrigeration system, an evaporator including upper and lower sections connected in series, a plurality of condenser sections, connections for flowing vaporous refrigerant fluid in series through said condenser sections and flowing liquid refrigerant fluid from each of said c0ndenser sections to one of said evaporator sections, connections for circulating an inert gas through said evaporator into which liquid refrigerant evaporates and diffuses, means for receiving liquid refrigerant and holding such liquid in contact with-circulating inert gas, a by-pass connection for vaporous refrigerant fluid around said condenser section from which liquid refrigerant fluid flows to said upper evaporator section, and means responsive to level of liquid in said receiving means for controlling said by-pass connection.

5. In a a refrigeration system, an evaporator, means to flow liquid refrigerant to different portions of said evaporator, connections 'for circulating an inert gas through said evaporator into which liquid evaporates and diffuses, means for receiving liquid refrigerant and holding such liquid in contact with circulatinginert gas, and

means responsive to level of liquid in said receiving means to vary the relative amount of liquid flowing to different portions of said evaporator.

6. In an. absorption refrigeration system containing auxiliary fluid, refrigerant fluid and an absorbent, an evaporator, means to supply liquid refrigerant fluid to said evaporator including a plurality of places of condensation connected for 'flcw of refrigerant fluid therethrough in series,

a by-pa-ss for refrigerant fluid shunting at least .a part of one of said places of condensation, and means to open and close'said Icy-pass with respect to flow of refrigerant fluid therethrough.

7. In a refrigeration system, an evaporator, means to supply liquid refrigerant to said evaporator including a plurality of places of condensation connected for flow of refrigerant fluid therethrough in series, connections for circulating an auxiliary fluid through said evaporator into which liquid refrigerant evaporates: and diffuses, a by-pass for refrigerant fluid shunting at least a part of one of said places of condensation, and means responsive to rise and fall of liquid. to open and close said by-pass with respect to flow of refrigerant fluid therethrough.

8. In a refrigeration system, an evaporator,

means to supply liquid refrigerant fluid to different portions of said evaporator including a plurality of condenser sections, connections for ci1'-' culation of auxiliary fluid through said evapo- 'rator, a chamber for holding liquid refrigerant in contact with auxiliary fluid, and means for changing the rate of circulation of refrigerant fluid in said condenser sections with changes of liquid level in said chamber due'to the differ- 1 ence in the rates at which liquid flows into and evaporates in said chamber.

9. In a refrigeration system, 'an evaporator and a plurality of condenser sections, connections for flowing vaporous refrigerant fluid to said condenser sections and liquid refrigerant fluid from the latter to diiferent portions of said evaporator, connections for circulating an auxiliary fluid through said evaporator into which liquid refrigerant evaporates and diffuses, a chamber connected to said evaporator for holding liquid refrigerant in contact with auxiliary fluid, and means for changing the rate of flow of refrigerant fluid in said condenser sections with changes of liquid level in said chamber.

10. A method of refrigeration with the aid of a system in which liquid refrigerant in an evaporator evaporates in the presence of and diffuses into an inert gas, that improvement which consists in flowing refrigerant fluid in a plurality of streams to a corresponding plurality of parts of said evaporator, accumulating liquid refrigerant at a place of accumulation in said system,

and diverting refrigerant fluid away from one of said streams to another responsive to change in the amount of liquid in said place of accumulation.

11. A method of refrigeration which includes flowing refrigerant fluid in liquid form into the presence of auxiliary fluid at a plurality of places, supplying said liquid refrigerant by condensing vaporous refrigerant .fluid to liquid at a place of condensation and dividing the liquid for flow to said places of evaporation in accordance with amounts of condensate formed in diiferent parts of said place of condensation, and selectively flowing the vapcrous refrigerant fluid to said place of condensation in a single stream or in a plurality of streams to said diflerent parts of said place of condensation responsive to change in a condition in one of said places of evaporation.

12. A method of refrigeration as set forth in claim 11, in which said auxiliary fluid is caused to flow from one of said places, of evaporation to another so that said one place of evaporation is at a lower temperature than the other, and said condition is the demand for refrigeration micro M. Umsramn. 

